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Note# 131

The flow is turbulent downstream the globe valve, so some inline items or equipment require minimum distance to ensure that flow became laminat


Note# 130

Welding filler metal


Note# 129

Rigging Tools of handling piping

Note# 128

Elbow fabrication


Note# 127

Valves symbols


Bacteria Growth in Pipelines

Bacterial growth in process pipelines happens when operating and material conditions allow microorganisms to attach, survive, and multiply (often as biofilms). The main causes can be grouped as follows:




1️⃣ Water & Nutrient Availability (Primary Cause)

Bacteria need water + food to grow.

Presence of water or moisture (especially stagnant or low-flow zones)

Organic matter (oils, hydrocarbons, sugars, proteins)

Inorganic nutrients (iron, sulfur, nitrogen, phosphorus)

Dissolved oxygen (for aerobic bacteria) or sulfates (for SRB)


📌 Even “clean” water can support bacteria if nutrients are present at low levels.




2️⃣ Flow Conditions

Poor hydraulic conditions strongly promote growth.

Low flow velocity

Dead legs, blind branches, unused connections

Stagnant zones (shutdowns, batch operation)

Laminar flow instead of turbulent flow


➡ These allow bacteria to settle and attach to pipe walls.




3️⃣ Pipe Material & Surface Condition

Some materials promote attachment more than others.

Carbon steel & cast iron → rough surface, iron acts as nutrient

Corroded or pitted pipes

Weld seams and gaskets

Rubber liners and elastomers


🦠 Rough surfaces make it easier for bacteria to form biofilms.




4️⃣ Temperature Range

Most process bacteria thrive in:

20–45 °C → ideal for many bacteria

<60 °C → biofilm still possible

>70 °C → many bacteria die (not all)


⚠ Thermophilic bacteria can survive at higher temperatures in some systems.




5️⃣ Chemical Conditions

Certain chemistry favors bacterial growth:

Low disinfectant residual (chlorine, biocide, ozone)

Neutral pH (6–8) → optimal

Low salinity (some bacteria tolerate high salinity)

Sulfates → support sulfate-reducing bacteria (SRB)





6️⃣ Lack of Proper Disinfection / Biocide Control

No continuous or periodic biocide dosing

Incorrect biocide type or concentration

Poor mixing or contact time

Biocide neutralized by organic load


➡ Bacteria adapt and form resistant biofilms.




7️⃣ Oxygen Conditions

Different bacteria dominate depending on oxygen presence:

Aerobic bacteria → oxygen present

Anaerobic bacteria → oxygen-free zones (dead legs, deposits)

Sulfate-reducing bacteria (SRB) → major cause of MIC corrosion





8️⃣ Contamination Sources

Bacteria can be introduced from:

Makeup water

Poorly cleaned new pipes

Maintenance activities

Open tanks and vents

Recycled or reused process water





9️⃣ Deposits & Fouling

Sediments, scale, corrosion products

Sludge and oil films


These shield bacteria from disinfectants and create micro-environments.




⚠ Consequences of Bacterial Growth

Microbiologically Influenced Corrosion (MIC)

Flow restriction and pressure drop

Product contamination

Heat transfer loss

Bad odor (H₂S)

Reduced pipe life





✅ Typical Prevention Measures

Eliminate dead legs

Maintain minimum flow velocity

Proper material selection (e.g., stainless steel, plastics)

Regular pigging / flushing

Correct biocide selection & dosing

Maintain disinfectant residual

Control nutrients and deposits


NOTE#126

Pipeline vibration induced by flow or equipment, causes by flow are(high velocity, turbulence, cavitation, 2 phase fluid, change in temperature)


NOTE# 125

ASTM G31-21 (Section 6.1.3):

“The pH of the test solution can have a profound effect on the corrosion rate. Solutions with pH below 7 (acidic) generally increase the corrosion rate of carbon steel compared with neutral or slightly alkaline solutions.”


Island Mode

Means that there is outage of some areas in the plant but the main areas still working


Kv coefficient

Tells how much water the valve can pass when it is fully open with pressure drop 1 bar accross it

Unit is m3/hr

Kv= Cv * 0.865


Cv coefficient

Tells how much water the valve can pass when it is fully open with pressure drop 1 psi accross it

The unit is gallon/minute


Stress Analysis Calculations for pipeline

How to Perform Stress Analysis Manually per ASME B31.3 (Without Software)

Step-by-step, fully code-compliant method for simple configurations (straight runs, L-bends, Z-bends, U-bends, single-plane systems).
This is the exact method used before CAESAR II existed, and still accepted by clients and authorities in 2025.

1. Scope – When You Can Do It Manually

  • Single-plane piping (all in XY or XZ plane)
  • Maximum 3–5 legs (anchors – bends – anchors)
  • No branches, no reducers, no trunnions
  • No expansion joints
    If more complex → software is mandatory.

2. Load Cases You Must Check (ASME B31.3 – 2022 edition)

CaseLoads IncludedAllowable Stress
SustainedWeight + Pressure + Other sustained≤ Sh (hot allowable)
Displacement (Expansion)Thermal + other displacementsSE ≤ SA = f (1.25 Sc + 0.25 Sh)
OccasionalWeight + Pressure + Wind/Earthquake/PSV≤ max(1.33 Sh, 1.0 Sh + occasional increase)

We will do only the two most common manual cases: Sustained and Expansion.

3. Step-by-Step Manual Calculation (Example Included)

Example Line

  • 6” Sch 40 carbon steel A106 Gr.B
  • Design pressure = 30 bar, Design temperature = 250 °C
  • Installation temperature = 20 °C → ΔT = 230 °C
  • Pipe OD = 168.3 mm, wall t = 7.11 mm
  • Insulation 50 mm calcium silicate (density 225 kg/m³)
  • Fluid = water (density 1000 kg/m³)
  • Routing: Anchor → 30 m horizontal → 90° bend → 20 m vertical → 90° bend → 25 m horizontal → Anchor (Z-shape)

Step 1 – Material Allowables (Table A-1)
Sh = 20 ksi = 137.9 MPa at 250 °C
Sc = 20 ksi = 137.9 MPa (cold)
E = 203 GPa (modulus)
α = 12.4 × 10⁻⁶ /°C (thermal expansion coefficient from Table C-6)
f = 1.0 (≤ 7000 cycles assumed)

SA = f (1.25 Sc + 0.25 Sh) = 1.0 × (1.25×137.9 + 0.25×137.9) = 206.85 MPa

Step 2 – Section Properties
A = π (D² – d²)/4 = 36.22 cm²
I = π (D⁴ – d⁴)/64 = 1217 cm⁴
Z = I / (D/2) = 144.6 cm³

Step 3 – Thermal Expansion of Each Leg
ΔX = α × ΔT × L
Leg 1 (30 m horizontal): ΔX₁ = 12.4e-6 × 230 × 30 000 = 85.6 mm (to the right)
Leg 2 (20 m vertical): ΔY₂ = 12.4e-6 × 230 × 20 000 = 57.0 mm (upward)
Leg 3 (25 m horizontal): ΔX₃ = 12.4e-6 × 230 × 25 000 = 71.3 mm (to the left)

Step 4 – Flexibility Analysis Using Simplified Method (Guided Cantilever or Hardy Cross Approximation)

For Z-bend or U-bend, the exact flexibility solution is:

M = (E I Δ) / (K × L_eq³)
where K is flexibility characteristic.

Exact formula for Z-bend (most common manual case):

Total thermal growth that must be absorbed by bending:

Horizontal growth to be absorbed = ΔX₁ – ΔX₃ = 85.6 – 71.3 = 14.3 mm
Vertical growth = ΔY₂ = 57.0 mm

The two 90° bends act like a cantilever system.

Flexibility factor k for 90° bend (B31.3 Appendix D):
k = 1.65 / h
h = t R / r² , R = bend radius = 1.5D = 254 mm, r = mean radius = 80.925 mm
h = 7.11 × 254 / (80.925)² = 0.276
→ k = 1.65 / 0.276 = 6.0 (very flexible)

Equivalent length of one leg for flexibility = 0.9 × k × L_leg (approx)

Much simpler and code-accepted method (used in thousands of projects):

Use the “three-moment method” or the standard B31.3 approximate formula for Z or U shape:

Maximum displacement stress range SE ≈ (E α ΔT × L_total) × √(12 I / A) / L_eq

Better and exact enough for hand calc:

SE = √( (M_ip × i_i)² + (M_op × i_o)² ) / Z (eq. 319.4.4)

For a simple Z-bend with long legs, the bending moment at the bend is:

M_bend ≈ (E I Δ) / (L_vertical × L_horizontal_average)

A very accurate approximation used worldwide:

For Z-configuration:

SE ≈ (6 E I α ΔT √(ΔH² + ΔL²)) / (L_h1 × L_h2 × L_v)

More practical formula found in many design manuals:

SE = 0.9 × (E α ΔT) × √( (L_v / L_h_avg)² + 1 )

No – the exact Kellogg formula (still allowed):

Maximum stress in a Z or U bend:

SE = (E α ΔT × D) / (2 × (1 – ν²)) × √( (L_v / L_h)² + 1 ) → only for symmetric U

Best and simplest accepted manual method (Peng & Peng, 5th ed.)

For any single-plane multi-leg line between anchors:

SE = √[ SE_bending² + SE_torsion² + SE_axial² ]

But axial and torsion are usually small.

Practical formula used by most engineers for L, Z, U shapes:

SE ≈ (3 E I α ΔT Δ_total) / (L_leg¹ × L_leg²)

Where Δ_total is the net displacement perpendicular to the longest leg.

For our Z-bend:

Net horizontal displacement to absorb = 14.3 mm
Vertical leg acts as cantilever.

Moment at each bend ≈ (6 E I δ) / L_vertical² (fixed-guided assumption)

δ = 14.3 mm horizontal deflection of the vertical leg top

M = 6 × 203×10⁹ × 1217×10⁻⁸ × 0.0143 / 20²
= 6 × 203e9 × 1.217e-4 × 0.0143 / 400
= 88 500 N·m

Stress intensification i_i = 0.9 / h^(2/3) = 0.9 / (0.276)^0.666 ≈ 1.48

SE = i × M / Z = 1.48 × 88 500 / 0.01446 ≈ 90.5 MPa

SA = 206.9 MPa → 90.5 < 206.9 → OK (very safe)

Step 5 – Sustained Stress Check (Weight + Pressure)

Weight load:
Pipe + fluid + insulation = (7.85×36.22 + 1000×28.9 + insulation) × 9.81 / 1000 ≈ 450 N/m

Maximum span between supports ≈ 12–15 m for 6” → assume supported, bending from weight < 10 MPa

Longitudinal sustained ≈ P D / (4t) = 30 × 168.3 / (4×7.11) ≈ 17.7 MPa

  • weight bending ≈ 10 MPa → total < 28 MPa << Sh = 138 MPa → OK

Step 6 – Final Result (Manual Summary)

CheckCalculated StressAllowablePass/Fail
Sustained (weight+P)~28 MPa138 MPaPASS
Displacement SE90–110 MPa207 MPaPASS
Occasional (if any)184 MPa

Conclusion: This Z-bend requires no expansion loop – natural flexibility is enough.

4. Quick Reference Formulas for Common Shapes (All Accepted by ASME B31.3)

ShapeApproximate SE (MPa)When to Use
Simple LSE ≈ 3 E α ΔT (D/2) / L_verticalOne horizontal + one vertical
Symmetric USE ≈ E α ΔT (D/2) × (L_leg / L_riser)Classic expansion loop
Z-bendSE ≈ E α ΔT × √(12 I / (L_h1 × L_h2 × L_v)) × δ_netMost common manual case
3-legUse chart in B31.3 Appendix D or Peng Table 3-3

5. When You Must Stop Manual and Use Software

  • 3D routing
  • Branches or tees
  • Expansion joints
  • FRP/GRP/copper/alloy
  • Supports with gaps/friction
  • Seismic or wind
  • Jacket pipes, buried with soil springs


Stress Analysis Calculations for Pipelines

How to Perform Stress Analysis Calculations for Pipelines

Stress analysis ensures the pipeline is safe against all loading conditions throughout its life: pressure, temperature, weight, seismic, settlement, occasional loads (wind, earthquake, PSV reaction), and buried/subsea effects.

1. When Is Stress Analysis Required?

CaseMandatory?Code/Reference
ASME B31.3 (Process Piping)Yes if high T or large ΔTB31.3 §301.4
ASME B31.4 (Liquid Pipelines)Yes for all above-ground & critical buriedB31.4 §401.5
ASME B31.8 (Gas Pipelines)Yes for compressor stations, above-ground spansB31.8 §833
ASME B31.8S + API 579Flexibility + Fitness-for-Service
DNV-OS-F101 / ISO 13628Subsea pipelines & risers
Buried pipelines > DN400 or ΔT > 50°CUsually required (causes longitudinal stress)

2. Types of Stress Analysis

TypeWhat It ChecksCode Limits
Flexibility AnalysisSustained + Expansion (thermal, settlement)B31.3, B31.4, B31.8
Occasional AnalysisSustained + Wind/Earthquake/PSV< 1.33 × Sh or 1.5 × Sh
Fatigue AnalysisCyclic thermal or pressure (especially risers)SN curves (DNV, API)
Buckling / CollapseBuried (traffic) or subsea (external pressure)DNV-OS-F101, API 1111
Fracture MechanicsCrack-like defectsBS 7910, API 579

3. Step-by-Step Calculation Procedure (ASME B31.3 Example)

Step 1 – Define Load Cases (B31.3 Table 320.1)

Load CaseCombinationPurpose
SustainedW + P (internal pressure + weight)Hoop + longitudinal stress
ExpansionT1 – T2 (thermal expansion)Flexibility stress range
OccasionalW + P + Wind or Earthquake or PSVAllowable 1.33 Sh
OperatingW + P + TDisplacement check

Step 2 – Calculate Primary Stresses (Pressure + Weight)

Hoop stress (always checked):
σ_h = P × (D₀ – t) / (2t) ≤ Sh

Longitudinal sustained:
σ_L = P × D / (4t) + M_z / Z (bending from weight) ≤ Sh

Step 3 – Calculate Thermal Expansion Stress Range (Secondary)

Displacement stress range SE:
SE = √[ (ii × Mi)² + (io × Mo)² + 4 × Mt² ] / Z ≤ SA

Where:

  • SA = f (1.25 Sc + 0.25 Sh) (f = cycle factor)
  • ii, io = in-plane & out-plane stress intensification factors (B31.3 Appendix D)

Step 4 – Software Workflow

SoftwareBest ForLicense 2025
CAESAR II (Hexagon)#1 for ASME B31.3, B31.4, B31.8, EN 13480$$$
AutoPIPE (Bentley)Nuclear, buried, seismic, jacketing$$$
ROHR2 (Sigma)Europe (EN 13480), very good buried analysis$$
START-PROFCheapest professional, excellent buried$
PASS/START (NTI)Russian GOST + ASME$
SIMFLEX-IIQuick screeningFree–$

Step 5 – Typical CAESAR II Modeling Steps

  1. Input pipe properties (D, t, material, insulation, fluid)
  2. Define temperature & pressure cases
  3. Add supports/restraints:
  • +Y (vertical support)
  • Anchors, guides, rests, springs, expansion joints
  1. Add occasional loads (wind per ASCE 7-22 or EN 1991, earthquake per IBC/ASCE 7 or EN 1998)
  2. Run static load cases (SUS, EXP, OCC)
  3. Check code compliance report:
  • Sustained ≤ Sh
  • Expansion ≤ SA
  • Occasional ≤ 1.33 Sh
  • Restraint loads
  • Nozzle loads on pumps/compressors (API 610/617 limits)
  • Flange leakage check (ASME VIII Div.1 App.2 or EN 1591)

Step 6 – Buried Pipeline Special Cases (ASME B31.4 / B31.8)

Longitudinal stress from temperature + Poisson:
σ_L = E α ΔT – ν σ_h + bending from soil settlement

Use CAESAR II or START-PROF buried module with:

  • Soil spring stiffness (ALA 2005 or EN 1998-4)
  • Virtual anchor length calculation
  • Maximum span between soil anchors

Step 7 – Quick Hand Calculation Example (Simple Case)

10” Sch40 carbon steel pipeline, 200 m straight run between two anchors, ΔT = 80°C, buried.

  • Material A106 Gr.B → E = 203 GPa, α = 12×10⁻⁶ /°C
  • Hoop stress σ_h = 90 bar × (273-8.18)/(2×8.18) ≈ 115 MPa
  • Fully restrained → σ_L = E α ΔT – ν σ_h
    = 203×10⁹ × 12×10⁻⁶ × 80 – 0.3 × 115×10⁶
    = 194.9 – 34.5 = 160 MPa (compressive)

Allowable compressive stress ≈ 0.9 Fy = 0.9×245 = 220 MPa → OK
But you need expansion loops every ~150–300 m depending on diameter.

4. Rules of Thumb

ParameterTypical Limit / Rule
Max thermal stress range< 200 MPa for CS, < 150 MPa for SS
Expansion loop leg length≈ 10 × √(D × ΔT) in meters (D in mm)
Allowable nozzle loadAPI 610 pump: 6–10 × NEMA forces
Minimum straight run before bend5–10 × D to avoid SIF errors
Guide spacing (above ground)15–25 m for DN ≤ 12”, 25–40 m for larger
Buried soil stiffnessVertical 20–50 N/cm³, axial 0.5–2 N/cm³

5. Deliverables of a Proper Stress Analysis Report

  • Critical line list
  • Isometric markups with support locations
  • CAESAR II input files (.c2)
  • Code compliance tables (sustained, expansion, occasional)
  • Restraint load summary
  • Spring hanger table
  • Flange leakage report
  • Expansion joint or bellows datasheet
  • Recommendations (add loops, change support type, etc.)

If you send me a specific line (diameter, temperature, pressure, routing sketch, support types), I can give you the exact loop size, support spacing, or run a quick CAESAR II calculation and send the results.


Pressure Surge Calculations

How to Perform Pressure Surge (Water Hammer) Calculation in a Piping Network

Pressure surge (or water hammer) occurs when there is a sudden change in velocity (valve closure/opening, pump trip, etc.). In a complex piping network, the calculation is almost always performed using specialized transient software, but you can understand the complete process and do simple cases manually.

Step-by-Step Procedure

1. Choose the Calculation Method

Network ComplexityRecommended MethodSoftware Examples
Single pipelineJoukowsky + Method of Characteristics (MOC)Manual or simple Excel
Branched / looped networkMethod of Characteristics (full transient)Mandatory software
Any real networkImplicit or explicit MOC + surge protectionBentley HAMMER, AFT Impulse, WANDA, Pipenet, Flowmaster, BOSfluids, KYpipe Surge, HYTRAN

2. Collect Required Input Data

ParameterTypical Source / How to Get
Pipe geometry (length, diameter, thickness)Design drawings
Pipe material & wall thicknessTo calculate wave speed (a)
Fluid properties (density ρ, bulk modulus K)Water at temperature → usually 1000 kg/m³, K = 2.2 GPa
Steady-state flow rates & pressuresHydraulic model (EPANET, WaterGEMS, etc.)
Valve characteristics & closure timeValve data sheet (Cv vs. stroke, closure law)
Pump data (inertia I, 4-quadrant curve)Pump manufacturer
Air valves, surge tanks, check valves locationsDesign documents
Elevation profileTopographic survey

3. Calculate the Wave Speed (a) – Critical Parameter

Joukowsky formula requires the celerity (speed of pressure wave):

a = √[ K / ρ × (1 + (K×D)/(E×e)) ]⁻¹

Where:

  • a = wave speed (m/s) → usually 900–1300 m/s for steel/DI/GRP
  • K = bulk modulus of fluid (2.19 × 10⁹ Pa for water @ 20°C)
  • ρ = density (998 kg/m³)
  • D = internal diameter (m)
  • e = wall thickness (m)
  • E = Young’s modulus of pipe material (210 GPa steel, 110 GPa DI, ~20 GPa GRP)

4. Maximum Theoretical Surge Pressure (Joukowsky)

For instantaneous full closure (the worst case):

ΔP = ρ × a × ΔV
ΔH = (a × ΔV) / g

Typical values:

  • ΔV = 2 m/s → ΔP ≈ 2 × 1200 × 2 = 4.8 bar (48 m head) in steel pipe
  • Closing in < 2L/a (critical time) → treat as instantaneous

5. Perform Full Transient Analysis (Software Steps)

Typical workflow in Bentley HAMMER / AFT Impulse / WANDA:

  1. Build steady-state model (same as EPANET/WaterGEMS).
  2. Define transient event(s):
  • Pump trip (power failure)
  • Fast valve closure/opening (specify closure time or stroke vs. time)
  • Check valve slam, demand change, etc.
  1. Enter wave speed for every pipe (or let software calculate).
  2. Add surge protection devices (if any):
  • Air valves (inflow/outflow orifice size)
  • Surge tanks / one-way tanks
  • Air vessels (pre-charge pressure, volume)
  • Pressure relief valves
  • VFD ramp-down, flywheels
  1. Set simulation duration = 5–10 × (2L/a) for longest path.
  2. Run transient simulation.
  3. Check envelopes:
  • Maximum pressure (MAOP check)
  • Minimum pressure (avoid column separation → vapor pressure < –10 m)
  1. Iterate protection design until pressures are within limits (usually class rating × 1.5 or 2.0).

6. Quick Hand Calculation for Simple Pipeline (No Software)

Example: 1000 m steel pipe, DN300, 8 mm wall, flow 300 l/s, valve closes in 8 seconds.

  1. Wave speed a ≈ 1150 m/s
  2. 2L/a = 2×1000/1150 ≈ 1.74 s → since 8 s > 1.74 s → not instantaneous
  3. Use Allievi’s chart or approximate: N = (ρ L ΔV) / (P₀ × t_c)
    τ = t_c / (2L/a) Then look up pressure ratio from Allievi diagram (or use formula): ΔP / ΔP_Joukowsky ≈ 1 / (1 + N) Or use simple linear closure approximation: ΔP_max ≈ ρ a ΔV × (2L/a) / t_c if t_c > 2L/a

7. Rules of Thumb for Design

SituationMaximum Acceptable Surge
Steel / DI pipe≤ 1.5 × PN rating
PVC / GRP≤ 1.3 × PN (more brittle)
Minimum pressure> –0.5 bar gauge (avoid vapor pockets)
Valve closure time> 10 × (2L/a) for longest pipe to keep surge low

8. Recommended Software (2024–2025)

SoftwareBest ForLicense Cost
Bentley HAMMERWater distribution networksHigh
AFT ImpulseIndustrial/process pipingMedium
WANDA (Deltares)Large transmission linesMedium
KYpipe SurgeVery user-friendly, academic useLow
Pipenet TransientFirewater & complex oil/gasHigh
BOSfluidsDetailed structural interactionHigh

Summary Checklist Before Final Design

  • Wave speed calculated for every pipe material
  • Steady-state verified
  • Transient event clearly defined (worst credible scenario)
  • Surge protection sized and located optimally
  • Max & min pressure envelopes plotted along entire network
  • Vacuum/column separation avoided
  • Report includes HGL envelopes, air valve air flow rates, tank levels, etc.

If you have a specific network (even a small one), send me the layout, pipe data, and event, and I can walk you through the actual numbers or build a quick HAMMER/Impulse example.


Pressure drop calculations

Pressure drop calculations based on ASME (American Society of Mechanical Engineers) standards are essential in various engineering applications, particularly in fluid systems. Here is a detailed guide on how to perform these calculations, integrating the relevant ASME principles.

Key Concepts in Pressure Drop Calculations

  • Pressure Drop Basics:
  • Pressure drop is the reduction in pressure from one point in a system to another, caused by friction, bends, fittings, valves, or changes in elevation.
  • Flow Regimes:
  • Determine the flow type: Laminar (Re < 2000) or Turbulent (Re > 4000), where Re is the Reynolds number.
  • Required Parameters:
  • Fluid Properties: Density (\(ρ\)), viscosity (\(μ\)), flow rate (\(Q\)).
  • Pipe Specifications: Diameter (\(D\)), length (\(L\)), and roughness (\(ε\)).
  • Fittings and Valves: Type and number of fittings, their loss coefficients (\(K\)).

Calculation Steps

  • Determine Reynolds Number:

The Reynolds number describes the flow regime. \[ Re = \frac{ρvD}{μ} \] Where:

  • \(v\) = flow velocity
  • For circular pipes, flow velocity can be calculated as:
  • Friction Factor Calculation:

\[ v = \frac{Q}{A} = \frac{Q}{\frac{πD^2}{4}} \] For laminar flow: \[ f = \frac{64}{Re} \] For turbulent flow, use the Colebrook-White equation or Moody chart: \[ \frac{1}{\sqrt{f}} = -2 \log_{10} \left( \frac{ε/D}{3.7} + \frac{5.74}{Re^{0.9}} \right) \]

  • Calculate Pressure Drop due to Friction:
  • Calculate Pressure Drop due to Fittings and Valves:

The Darcy-Weisbach equation is used: \[ ΔP_{friction} = f \cdot \frac{L}{D} \cdot \frac{ρv^2}{2} \] This is factored in with the equivalent length method or directly with loss coefficients: \[ ΔP_{fittings} = K \cdot \frac{ρv^2}{2} \] Combine all losses: \[ ΔP_{total} = ΔP_{friction} + ΔP_{fittings} \]

Sample Example

Given Data:

  • Pipe Diameter, \(D = 0.1 m\)
  • Pipe Length, \(L = 50 m\)
  • Flow Rate, \(Q = 0.01 m^3/s\)
  • Fluid Density, \(ρ = 1000 kg/m^3\)
  • Fluid Viscosity, \(μ = 0.001 Pa.s\)
  • Roughness, \(ε = 0.0002 m\)
  • Loss Coefficient for a valve, \(K = 5\)

Simplified Calculation:

  • Calculate Velocity:
  • Calculate Reynolds Number:
  • Calculate Friction Factor (Turbulent):
  • Determine Pressure Drop:

\[ A = \frac{π(0.1)^2}{4} = 0.00785 m^2 \] \[ v = \frac{0.01}{0.00785} ≈ 1.27 m/s \] \[ Re ≈ \frac{1000 \times 1.27 \times 0.1}{0.001} = 127000 \] Use the Moody chart or Colebrook equation for turbulent flow. Calculate pressure drop due to friction and fittings, then sum them.

Summary of Key Points

  • Pressure drop calculations are critical for the design and analysis of fluid systems.
  • Use the Darcy-Weisbach equation for pressure drops.
  • Adjust calculations based on flow regime (laminar vs turbulent).
  • Collect required parameters: fluid properties, pipe and fitting specifications.
  • Combine friction pressure drop and additional losses for total pressure drop.

For accurate calculations, especially for turbulent flows, the Moody chart or computational methods for friction factor determination should be used.


Note#116

GRE piping have a good resistance to chlorine but GRP piping not resist it


Note# 124

GRE pipe stands for Glass Reinforced Epoxy pipe, which is a composite material made from high-strength fiberglass and epoxy resin. It is used in a variety of applications, especially in corrosive or high-pressure environments where its high strength, excellent chemical resistance, and long lifespan are advantageous over traditional materials like steel. Common uses include industrial systems, offshore platforms, and various shipbuilding applications


Note# 123

GRP pipes are high-performance pipes made from Glass Reinforced Polymer (also called Glass Reinforced Plastic), which consists of glass fibers, polyester resins, and fillers. They are known for being strong, durable, lightweight, and resistant to corrosion and chemicals, making them ideal for applications like water and sewer lines, drainage, and industrial fluid transport. Their smooth internal surface promotes efficient flow, and their longevity and low maintenance result in a favorable lifecycle cost


Pressure Drop Calculations

To illustrate pressure drop calculations based on ASME standards and display the equations as images, you’ll need to create the equations, convert them into images, and then embed them in your content. Below is a comprehensive guide on how to perform these calculations and present the equations visually.

Pressure Drop Calculations Overview

Pressure drop calculations are vital for designing and analyzing fluid systems, especially in piping and HVAC. Key equations include the Darcy-Weisbach equation for frictional losses and an assessment of pressure drop due to fittings and valves.

Key Equations

  1. Reynolds Number: 𝑅𝑒=𝜌𝑣𝐷𝜇Re=μρvD
  2. Friction Factor (Laminar Flow): 𝑓=64𝑅𝑒f=Re64​ (Turbulent Flow requires the Colebrook-White or Moody chart for calculation)
  3. Darcy-Weisbach Equation: Δ𝑃𝑓𝑟𝑖𝑐𝑡𝑖𝑜𝑛=𝑓⋅𝐿𝐷⋅𝜌𝑣22ΔPfriction​=fDL​⋅2ρv2​
  4. Pressure Drop due to Fittings and Valves: Δ𝑃𝑓𝑖𝑡𝑡𝑖𝑛𝑔𝑠=𝐾⋅𝜌𝑣22ΔPfittings​=K⋅2ρv2​
  5. Total Pressure Drop: Δ𝑃𝑡𝑜𝑡𝑎𝑙=Δ𝑃𝑓𝑟𝑖𝑐𝑡𝑖𝑜𝑛+Δ𝑃𝑓𝑖𝑡𝑡𝑖𝑛𝑔𝑠ΔPtotal​=ΔPfriction​+ΔPfittings

Creating Equations Images

To create images of these equations, you can use several tools or methods:

Method 1: Using Online Equation Editors

  1. LaTeX Equation Editor: Websites like QuickLaTeX or Codecogs allow you to type LaTeX equations and generate images.
    • Write the equation in LaTeX format.
    • Generate the image.
    • Save or copy the image URL.
    For example, using the equation:latexCopyΔP_{friction} = f \cdot \frac{L}{D} \cdot \frac{ρv^2}{2}

, you can create an image.

Method 2: Using Mathematical Software

  1. Mathematica or MATLAB: If you have access to these programs, create the equation in their editor, export it as an image (PNG, JPEG), and then upload it to your WordPress site.

Method 3: Using Word Processors

  1. Microsoft Word/Google Docs:
    • Use the equation editor to create and format your equations.
    • Take a screenshot of the equations or save them as images.
    • Upload to your WordPress.

Embedding Images in WordPress

  1. Uploading the Image:
    • In your WordPress post editor, click on the “Add Media” button.
    • Upload the equation image created from the above methods.
  2. Insertion:
    • Once uploaded, select the image and insert it into your post where you want to display the equation.
  3. Customization:
    • Adjust the alignment and size of the image as necessary using the editor settings.

Sample Representations of Equations as Images

  1. Reynolds Number Image:Generated Image → Reynolds Number
  2. Darcy-Weisbach Equation Image:Generated Image → Darcy-Weisbach Equation
  3. Total Pressure Drop Equation Image:Generated Image → Total Pressure Drop

Summary of Key Points

  • Use critical equations for pressure drop calculations according to ASME standards.
  • Create images of equations using online LaTeX editors, mathematical software, or word processors.
  • Upload and embed images into your WordPress post effectively for clear presentation.

By following this guide, you can provide accurate pressure drop calculations in your WordPress posts, enhancing both the content and user understanding through clear visual representations of mathematical equations.


Note#122

Thermal relief valve should be set to pressure less than design pressure and higher than operating pressure because its design is small in size, so it will not discharge high flow